CN107490148A - Air conditioner and its efficiency computational methods - Google Patents

Air conditioner and its efficiency computational methods Download PDF

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Publication number
CN107490148A
CN107490148A CN201710776014.6A CN201710776014A CN107490148A CN 107490148 A CN107490148 A CN 107490148A CN 201710776014 A CN201710776014 A CN 201710776014A CN 107490148 A CN107490148 A CN 107490148A
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msub
heat exchanger
mrow
refrigerant
temperature
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陈新
张�浩
戚文端
杨亚新
刘燕飞
汪亚涛
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GD Midea Air Conditioning Equipment Co Ltd
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Guangdong Midea Refrigeration Equipment Co Ltd
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Abstract

The invention discloses a kind of air conditioner and its efficiency computational methods, the described method comprises the following steps：Obtain current working, the power and the housing heat dissipation capacity Q of air conditioner power consumption and compressor of compressor of air conditionerloss；Obtain the gas returning port temperature t in compressor1, exhaust port temperatures t2And tonifying Qi temperature t8And the first end temperature t of outdoor heat exchanger4With the first end temperature t of indoor heat exchanger7；When the current working of air conditioner is cooling condition, according to t1、t2、t4、t7And t8The refrigerant enthalpy h of gas returning port is generated respectively1, exhaust outlet refrigerant enthalpy h2, outdoor heat exchanger first end refrigerant enthalpy h4, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”；According to the power of compressor, Qloss h1、h2、h4、h7、h8’And h8”Generate the refrigerating capacity of air conditioner；And the efficiency of air conditioner is generated according to air conditioner power consumption and refrigerating capacity.

Description

Air conditioner and its efficiency computational methods
Technical field
The present invention relates to air conditioner technical field, the efficiency computational methods of more particularly to a kind of air conditioner, a kind of air conditioner With a kind of non-transitorycomputer readable storage medium.
Background technology
As country increasingly payes attention to energy-conservation, consumer comfortably requires also more and more higher to the energy-conservation of air conditioner.Mesh Before, during air conditioner is run, due to that can not detect the situation of change of energy efficiency of air conditioner in real time, thus air conditioner is difficult to tie up Hold in preferable running status, so that refrigeration, heating effect and energy-efficient performance are not ideal enough.
The content of the invention
It is contemplated that at least solves one of technical problem in above-mentioned technology to a certain extent.
Therefore, first purpose of the present invention is the efficiency computational methods for proposing a kind of air conditioner, can be accurate in real time Ground detects the efficiency of air conditioner.
Second object of the present invention is to propose a kind of air conditioner.
Third object of the present invention is to propose a kind of non-transitorycomputer readable storage medium.
Fourth object of the present invention is the efficiency computational methods for proposing another air conditioner.
The 5th purpose of the present invention is to propose another air conditioner.
The 6th purpose of the present invention is to propose another non-transitorycomputer readable storage medium.
To reach above-mentioned purpose, first aspect present invention embodiment proposes a kind of efficiency computational methods of air conditioner, bag Include following steps：Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；Obtain the housing of compressor Heat dissipation capacity Qloss；Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust port temperatures t2、 The outdoor heat exchanger first end temperature t of outdoor heat exchanger first end4, indoor heat exchanger first end indoor heat exchanger first end temperature Spend t7With the tonifying Qi temperature t of compressor tonifying Qi entrance8, wherein, the gas returning port temperature t1According to the indoor heat exchanger first end Temperature t7Generated with the running frequency f of compressor；When the current working of the air conditioner is cooling condition, according to the compression The gas returning port temperature t of gas returning port in machine1Generate the refrigerant enthalpy h of gas returning port1, according to the exhaust of exhaust outlet in the compressor Mouth temperature t2Generate the enthalpy h of the refrigerant of exhaust outlet2, according to the outdoor heat exchanger first end of the outdoor heat exchanger first end Temperature t4Generate the refrigerant enthalpy h of outdoor heat exchanger first end4, according to the indoor heat exchanger of the indoor heat exchanger first end First end temperature t7Generate the refrigerant enthalpy h of indoor heat exchanger first end7With the fill temperature according to the compressor tonifying Qi entrance Spend t8Generation fills into the gaseous refrigerant enthalpy h of compressor respectively8’With the liquid refrigerant enthalpy h of flash vessel8”；According to the pressure The housing heat dissipation capacity Q of the power of contracting machine, the compressorloss, the gas returning port refrigerant enthalpy h1, the exhaust outlet system The enthalpy h of cryogen2, the outdoor heat exchanger first end refrigerant enthalpy h4, the indoor heat exchanger first end refrigerant enthalpy Value h7, the gaseous refrigerant enthalpy h for filling into compressor8’With the liquid refrigerant enthalpy h of the flash vessel8”Generate air conditioner Refrigerating capacity；And the efficiency of the air conditioner is generated according to the air conditioner power consumption and the refrigerating capacity.
The efficiency computational methods of air conditioner according to embodiments of the present invention, current working, the compression of air conditioner are obtained first The housing heat dissipation capacity of the power of machine, air conditioner power consumption and compressor, and obtain the gas returning port temperature of gas returning port in compressor The exhaust port temperatures of exhaust outlet, the outdoor heat exchanger first end temperature of outdoor heat exchanger first end, indoor heat exchange in degree, compressor The indoor heat exchanger first end temperature of device first end and the tonifying Qi temperature of compressor tonifying Qi entrance.When the current working of air conditioner is During cooling condition, the refrigerant enthalpy of above-mentioned each temperature detecting point is generated according to the temperature of above-mentioned each temperature detecting point, so The power of compressor, the housing heat dissipation capacity of compressor, the refrigerant enthalpy and air conditioner of above-mentioned each temperature detecting point are combined afterwards Power consumption obtains the efficiency of air conditioner.Thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating according to sky The running status of the real-time energy efficiency optimization air conditioner of device is adjusted, reaches energy-conservation and improves the purpose of refrigeration.
In addition, the efficiency computational methods of the air conditioner proposed according to the above embodiment of the present invention can also have following add Technical characteristic：
According to one embodiment of present invention, the gas returning port temperature t according to gas returning port in the compressor1Generation institute State the refrigerant enthalpy h of gas returning port1Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According to institute State gas returning port temperature t1With the indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1；According to the indoor heat exchanger Middle portion temperature t6Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；According to the suction superheat Δ t1With indoor heat exchange Device middle portion temperature t6Generate the modifying factor D of gas returning port refrigerant enthalpy1；According to the modifying factor of the gas returning port refrigerant enthalpy Sub- D1, the saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy h1。
According to one embodiment of present invention, the enthalpy of saturation refrigerant under the suction temperature is generated according to below equation hAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
According to one embodiment of present invention, the modifying factor of the gas returning port refrigerant enthalpy is generated according to below equation D1：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the indoor heat exchanger first end according to the indoor heat exchanger first end Temperature t7Generate the refrigerant enthalpy h of the indoor heat exchanger first end7Specifically include：According to the indoor heat exchanger first end Temperature t7With the indoor heat exchanger middle portion temperature t6Generate degree of superheat Δ t7；According to the degree of superheat Δ t7Changed with the interior Hot device middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；According to the indoor heat exchanger The modifying factor D of one end refrigerant enthalpy7With the enthalpy h of the saturation refrigerantAir-breathing saturationGenerate the refrigerant enthalpy h7。
According to one embodiment of present invention, the indoor heat exchanger first end refrigerant enthalpy is generated according to below equation Modifying factor D7：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the exhaust port temperatures t according to exhaust outlet in the compressor2Generation institute State the enthalpy h of the refrigerant of exhaust outlet2Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；According to The outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；According in the compressor The exhaust port temperatures t of exhaust outlet2With the outdoor heat exchanger middle portion temperature t3Generate discharge superheat Δ t2；According to the exhaust Degree of superheat Δ t2With the outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of exhaust outlet refrigerant enthalpy2；According to described Modifying factor D2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the enthalpy h of the refrigerant of the exhaust outlet2。
According to one embodiment of present invention, the modifying factor of the exhaust outlet refrigerant enthalpy is generated according to below equation D2：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the refrigerant enthalpy of the outdoor heat exchanger first end is generated according to below equation Value h4：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
According to one embodiment of present invention, the refrigerating capacity of the air conditioner is generated according to below equation：
Wherein, QRefrigerating capacityFor the Air conditioner refrigerating capacity, PCompressorFor compressor horsepower.
To reach above-mentioned purpose, second aspect of the present invention embodiment proposes a kind of air conditioner, and it includes memory, processing Device and the computer program that can be run on the memory and on the processor is stored in, meter described in the computing device During calculation machine program, the efficiency computational methods for the air conditioner that first aspect present invention embodiment proposes are realized.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.
To reach above-mentioned purpose, third aspect present invention embodiment proposes a kind of non-transitory computer-readable storage medium Matter, is stored thereon with computer program, and the computer program realizes first aspect present invention embodiment when being executed by processor The efficiency computational methods of the air conditioner of proposition.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of refrigeration.
To reach above-mentioned purpose, fourth aspect present invention embodiment proposes the efficiency computational methods of another air conditioner, Comprise the following steps：Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；Obtain the shell of compressor Body heat dissipation capacity Qloss；Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust port temperatures t2, outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3, the end of indoor heat exchanger second the second end of indoor heat exchanger temperature t5, indoor heat exchanger first end indoor heat exchanger first end temperature t7With the tonifying Qi temperature t of compressor tonifying Qi entrance8, wherein, The gas returning port temperature t1According to the outdoor heat exchanger middle portion temperature t3Generated with the running frequency f of compressor；When the air-conditioning When the current working of device is heating condition, according to the gas returning port temperature t of gas returning port in the compressor1Generate the refrigeration of gas returning port Agent enthalpy h1, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate the enthalpy h of the refrigerant of exhaust outlet2, according to institute State the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generate the refrigerant enthalpy h at the end of indoor heat exchanger second5, According to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end7Generate the refrigerant of indoor heat exchanger first end Enthalpy h7With the tonifying Qi temperature t according to the compressor tonifying Qi entrance8Generation fills into the gaseous refrigerant enthalpy of compressor respectively h8’With the liquid refrigerant enthalpy h of flash vessel8”；According to the power of the compressor, the housing heat dissipation capacity Q of the compressorloss、 The refrigerant enthalpy h of the gas returning port1, the exhaust outlet refrigerant enthalpy h2, the end of indoor heat exchanger second refrigeration Agent enthalpy h5, the indoor heat exchanger first end refrigerant enthalpy h7, the gaseous refrigerant enthalpy h for filling into compressor8’ With the liquid refrigerant enthalpy h of the flash vessel8”Generate the heating capacity of air conditioner；And according to the air conditioner power consumption and The heating capacity generates the efficiency of the air conditioner.
The efficiency computational methods of air conditioner according to embodiments of the present invention, current working, the compression of air conditioner are obtained first The housing heat dissipation capacity of the power of machine, air conditioner power consumption and compressor, and obtain the gas returning port temperature of gas returning port in compressor The exhaust port temperatures of exhaust outlet, the second end of indoor heat exchanger temperature at the end of indoor heat exchanger second, indoor heat exchange in degree, compressor The indoor heat exchanger first end temperature t of device first end7With the tonifying Qi temperature of compressor tonifying Qi entrance.When the current working of air conditioner For heating condition when, the refrigerant enthalpy of above-mentioned each temperature detecting point is generated according to the temperature of above-mentioned each temperature detecting point, The refrigerant enthalpy and air-conditioning of the housing heat dissipation capacity of power, compressor then in conjunction with compressor, above-mentioned each temperature detecting point Device power consumption obtains the efficiency of air conditioner.Thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating according to The running status of the real-time energy efficiency optimization air conditioner of air conditioner, reaches energy-conservation and improves the purpose of heating effect.
In addition, the efficiency computational methods of the air conditioner proposed according to the above embodiment of the present invention can also have following add Technical characteristic：
According to one embodiment of present invention, the gas returning port temperature t according to gas returning port in the compressor1Generation institute State the refrigerant enthalpy h of gas returning port1Specifically include：According to the gas returning port temperature t1With the outdoor heat exchanger middle portion temperature t3 Generate suction superheat Δ t1；According to the suction superheat Δ t1With the outdoor heat exchanger middle portion temperature t3Generate gas returning port The modifying factor D of refrigerant enthalpy1；According to the outdoor heat exchanger middle portion temperature t3Generate saturation refrigerant under suction temperature Enthalpy hAir-breathing saturation；According to the modifying factor D of the gas returning port refrigerant enthalpy1, under the suction temperature saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy h of the gas returning port1。
According to one embodiment of present invention, the enthalpy of saturation refrigerant under the suction temperature is generated according to below equation hAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
According to one embodiment of present invention, the modifying factor of the gas returning port refrigerant enthalpy is generated according to below equation D1：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the exhaust port temperatures t according to exhaust outlet in the compressor2Generation institute State the enthalpy h of the refrigerant of exhaust outlet2Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；According to Indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the exhaust port temperatures t of exhaust outlet in the compressor2Generation Discharge superheat Δ t2；According to the discharge superheat Δ t2With the indoor heat exchanger middle portion temperature t6Generate exhaust outlet refrigeration The modifying factor D of agent enthalpy2；According to the outdoor heat exchanger middle portion temperature t6Generate the enthalpy of saturation refrigerant under delivery temperature hIt is vented saturation；According to the modifying factor D of the exhaust outlet refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h of the exhaust outlet2。
According to one embodiment of present invention, the modifying factor of the exhaust outlet refrigerant enthalpy is generated according to below equation D2：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the indoor heat exchanger first end according to the indoor heat exchanger first end Temperature t7Generate the refrigerant enthalpy h of the indoor heat exchanger first end7Specifically include：In the middle part of the indoor heat exchanger Indoor heat exchanger middle portion temperature t6With the indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7；According to the degree of superheat Δt7With the indoor heat exchanger middle portion temperature t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7；According to The modifying factor D of the indoor heat exchanger first end refrigerant enthalpy7, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h7。
According to one embodiment of present invention, the indoor heat exchanger first end refrigerant enthalpy is generated according to below equation Modifying factor D7：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
According to one embodiment of present invention, the refrigerant enthalpy at the end of indoor heat exchanger second is calculated according to below equation Value h5：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
According to one embodiment of present invention, the heating capacity of the air conditioner is generated according to equation below：
Wherein, QHeating capacityFor the heating capacity of air conditioner, PCompressorFor compressor horsepower.
To reach above-mentioned purpose, fifth aspect present invention embodiment proposes another air conditioner, and it includes memory, place Manage device and be stored in the computer program that can be run on the memory and on the processor, described in the computing device During computer program, the efficiency computational methods for the air conditioner that fifth aspect present invention embodiment proposes are realized.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.
To reach above-mentioned purpose, sixth aspect present invention embodiment proposes the computer-readable storage of another non-transitory Medium, is stored thereon with computer program, and the computer program realizes that fifth aspect present invention is implemented when being executed by processor The efficiency computational methods for the air conditioner that example proposes.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of heating effect.
Brief description of the drawings
Fig. 1 is the structural representation of air conditioner according to an embodiment of the invention；
Fig. 2 is the flow chart of the efficiency computational methods of air conditioner according to an embodiment of the invention；And
Fig. 3 is the flow chart of the efficiency computational methods of air conditioner in accordance with another embodiment of the present invention.
Embodiment
Embodiments of the invention are described below in detail, the example of the embodiment is shown in the drawings, wherein from beginning to end Same or similar label represents same or similar element or the element with same or like function.Below with reference to attached The embodiment of figure description is exemplary, it is intended to for explaining the present invention, and is not considered as limiting the invention.
Efficiency computational methods, air conditioner, the non-transitory of the air conditioner of the embodiment of the present invention described below in conjunction with the accompanying drawings The efficiency computing system of computer-readable recording medium and air conditioner.
In an embodiment of the present invention, air conditioner can be single-stage vapor compression formula air conditioner.
As shown in figure 1, the air conditioner of the embodiment of the present invention, it may include compressor 100, four-way valve 200, outdoor heat exchanger 300th, first throttle element 400, the second restricting element 700, flash vessel 600 and indoor heat exchanger 500.
When the current working of air conditioner is cooling condition, the exhaust outlet of compressor 100 by the A1 ends of four-way valve 200 and A2 ends are directly connected with outdoor heat exchanger 300, and refrigerant is flowed to as shown in the solid arrow in Fig. 1.Specifically, from compressor 100 Exhaust outlet discharge high pressure gaseous refrigerant by four-way valve 200 A1 ends and A2 ends flow into outdoor heat exchanger 300 (now As condenser), turn into HTHP liquid refrigerant, HTHP liquid refrigerant warp after outdoor heat exchanger 300 condenses heat release Turn into low-temp low-pressure liquid refrigerants after the reducing pressure by regulating flow of second restricting element 700, low-temp low-pressure liquid refrigerants passes through flash vessel 600 First port flows into flash vessel 600, and a part of liquid refrigerants quickly becomes gaseous coolant in flash vessel 600, and from flash vessel 600 second port enters compressor 100 and carries out tonifying Qi to compressor 100, so as to improve air conditioner operating efficiency, remaining liquid State refrigerant flows out from the 3rd port of flash vessel 600, and is getting in heat exchange after the reducing pressure by regulating flow of first throttle element 400 Device 500 (being now evaporator), turn into low-temp low-pressure gaseous coolant, low-temp low-pressure gas after the evaporation endothermic of indoor heat exchanger 500 A4 end of the state refrigerant through four-way valve 200 and A3 ends flow into the gas returning port of compressor 100, pass through the low of the gas returning port of compressor 100 Warm low-pressure gaseous refrigerant enters compressor 100, so far completes refrigerative circle system.
When the current working of air conditioner is heating condition, the exhaust outlet of compressor 100 by the A1 ends of four-way valve 200 and A4 ends are directly connected with indoor heat exchanger 500, and refrigerant is flowed to as shown in the dotted arrow in Fig. 1.Specifically, from compressor 100 Exhaust outlet discharge high pressure gaseous refrigerant by four-way valve 200 A1 ends and A4 ends flow into indoor heat exchanger 500 (now As condenser), turn into HTHP liquid refrigerant, HTHP liquid refrigerant warp after indoor heat exchanger 500 condenses heat release Turn into low-temp low-pressure liquid refrigerants after the reducing pressure by regulating flow of first throttle element 400, low-temp low-pressure liquid refrigerants passes through flash vessel 600 3rd port flows into flash vessel 600, and a part of liquid refrigerants quickly becomes gaseous coolant in flash vessel 600, and from flash vessel 600 second port enters compressor 100 and carries out tonifying Qi to compressor 100, so as to improve air conditioner operating efficiency, remaining liquid State refrigerant flows out from the first port of flash vessel 600, and is entering outdoor heat exchange after the reducing pressure by regulating flow of the second restricting element 700 Device 300 (being now evaporator), turn into low-temp low-pressure gaseous coolant, low-temp low-pressure gas after the evaporation endothermic of outdoor heat exchanger 300 A2 end of the state refrigerant through four-way valve 200 and A3 ends flow into the gas returning port of compressor 100, pass through the low of the gas returning port of compressor 100 Warm low-pressure gaseous refrigerant enters compressor 100, so far completes heating cyclic process.
Fig. 2 is the flow chart of the efficiency computational methods of air conditioner according to an embodiment of the invention.As shown in Fig. 2 this The efficiency computational methods of the air conditioner of inventive embodiments, it may include following steps：
S101, obtain the current working of air conditioner, the power of compressor and air conditioner power consumption.
Specifically, the current working of air conditioner, the power of compressor can be monitored in real time by the electric-control system of air conditioner PCompressorWith air conditioner power consumption PPower consumption。
S102, obtain the housing heat dissipation capacity Q of compressorloss；
According to one embodiment of present invention, the housing heat dissipation capacity Q of compressor can be calculated by convection current, radiation formulaloss, The housing heat dissipation capacity Q of compressor can be specifically generated according to following formula (1)loss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t9+273.15)4+(9.4+0.052×(t2-t9))× ACompressor×(t2-t9) (1)
Wherein, ACompressorFor the surface area of compressor housing, it can wait acquisition by looking into pressure contracting type number；t2For compressor The exhaust port temperatures of middle exhaust outlet, it can be by setting the temperature sensor (as shown in Figure 1 02) of exhaust outlet within the compressor Detection obtains；t9For the temperature at outdoor heat exchanger fin, i.e. outdoor environment temperature, it can be by being disposed in the outdoor heat exchanger wing Outdoor temperature sensor (as shown in Figure 1 09) detection at piece and in air obtains.
S103, obtain the gas returning port temperature t of gas returning port in compressor1, in compressor exhaust outlet exhaust port temperatures t2, room The outdoor heat exchanger first end temperature t of external heat exchanger first end4, indoor heat exchanger first end indoor heat exchanger first end temperature t7With the tonifying Qi temperature t of compressor tonifying Qi entrance8, wherein, gas returning port temperature t1According to indoor heat exchanger first end temperature t7And pressure The running frequency f generations of contracting machine.
In an embodiment of the present invention, can be by setting temperature sensor respectively in corresponding temperature test point to obtain the temperature Spend the temperature of test point.
Specifically, as shown in figure 1, can be by setting the temperature sensor of exhaust outlet within the compressor (as shown in Figure 1 02) exhaust port temperatures t is obtained2；Obtained by the temperature sensor (as shown in Figure 1 04) for being disposed in the outdoor heat exchanger first end Outdoor heat exchanger first end temperature t4；By the temperature sensor (as shown in Figure 1 07) for being disposed in the interior heat exchanger first end Obtain indoor heat exchanger first end temperature t7；It is (as shown in Figure 1 by the temperature sensor for being arranged on compressor tonifying Qi entrance 08) the tonifying Qi temperature t of compressor tonifying Qi entrance is obtained8.Then can be according to outdoor heat exchanger middle portion temperature t3With the operation of compressor Frequency f generation gas returning port temperature t1。
Wherein, above-mentioned each temperature sensor effectively contacts with the refrigerant tube wall of corresponding temperature test point, is testing During the temperature of refrigerant tube wall, refrigerant tube wall can take Insulation, and the installation site of temperature sensor is as close to temperature Spend test point.For example, temperature sensor can be arranged on to corresponding temperature detecting point and be close to copper pipe, and by being incubated glue Band is wound sealing to copper pipe.Thereby, it is possible to improve the reliability and accuracy of temperature detection.
According to one embodiment of present invention, can be according to following formula when the current working of air conditioner is cooling condition (2) gas returning port temperature t is generated1：
t1=a*t7+b*f (2)
Wherein, f is compressor operating frequency, and a, b are fitting coefficient, and a, b can obtain according to lot of experimental data, can be led to The electric-control system for crossing air conditioner monitors the running frequency of compressor in real time.
S104, when the current working of air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in compressor1 Generate the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the refrigerant of exhaust outlet Enthalpy h2, according to the outdoor heat exchanger first end temperature t of outdoor heat exchanger first end4Generate the refrigeration of outdoor heat exchanger first end Agent enthalpy h4, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7Generate the system of indoor heat exchanger first end Cryogen enthalpy h7With the tonifying Qi temperature t according to compressor tonifying Qi entrance8Generation fills into the gaseous refrigerant enthalpy of compressor respectively h8’With the liquid refrigerant enthalpy h of flash vessel8”。
Herein it should be noted that when the current working of air conditioner is cooling condition, outdoor heat exchanger makees condenser, room External heat exchanger first end is condensator outlet, and indoor heat exchanger makees evaporator, and indoor heat exchanger first end is evaporator outlet, room The interior end of heat exchanger second is evaporator inlet.
Specifically, during air conditioner works, because the state of the refrigerant of different temperatures test point is different, therefore The enthalpy of the refrigerant of different temperatures test point is different.In one embodiment of the invention, rule of thumb formula can calculate To the enthalpy of refrigerant.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1, exhaust outlet refrigerant enthalpy h2, outdoor heat exchanger first end refrigerant enthalpy h4, indoor heat exchanger first end refrigerant enthalpy h7, fill into compressor Gaseous refrigerant enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”Detailed process.
Wherein, for the refrigerant enthalpy h of gas returning port in compressor1, when the current working of air conditioner is cooling condition, The refrigerant superheat of the gas returning port of compressor, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined1。
According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in compressor1Generate the system of gas returning port Cryogen enthalpy h1Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6, and according to gas returning port temperature t1 With indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1, then according to indoor heat exchanger middle portion temperature t6Generate air-breathing At a temperature of saturation refrigerant enthalpy hAir-breathing saturation, subsequently according to suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Generation The modifying factor D of gas returning port refrigerant enthalpy1, finally according to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant Enthalpy hAir-breathing saturationGenerate refrigerant enthalpy h1。
Further, the modifying factor D of gas returning port refrigerant enthalpy is generated according to following formula (3)1：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, room can be obtained by being disposed in the interior the temperature sensor (as shown in Figure 1 06) in the middle part of heat exchanger Interior heat exchanger middle portion temperature t6。
Getting gas returning port temperature t1With indoor heat exchanger middle portion temperature t6Afterwards, air-breathing mistake is generated according to following formula (4) Temperature Δ t1：
Δt1=t1-t6 (4)
Getting suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Afterwards, return-air is generated according to above-mentioned formula (3) The modifying factor D of mouth refrigerant enthalpy1, then can be according to the enthalpy of saturation refrigerant under following formula (5) generation suction temperature hAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Finally, according to the modifying factor D of gas returning port refrigerant enthalpy1, saturation refrigerant enthalpy hAir-breathing saturationGenerate refrigerant Enthalpy h1, h1=D1·hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7, when the current working of air conditioner is refrigeration work During condition, the refrigerant superheat of indoor heat exchanger first end, the position refrigerant superheat degree can be combined and calculate indoor heat exchanger first The refrigerant enthalpy h at end7。
According to one embodiment of present invention, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7It is raw Into the refrigerant enthalpy h of indoor heat exchanger first end7Specifically include：According to indoor heat exchanger first end temperature t7With indoor heat exchange Device middle portion temperature t6Generate degree of superheat Δ t7, and according to degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Generate indoor heat exchange The modifying factor D of device first end refrigerant enthalpy7, and the modifying factor D according to indoor heat exchanger first end refrigerant enthalpy7 With the enthalpy h of saturation refrigerantAir-breathing saturationGenerate refrigerant enthalpy h7。
Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to below equation (6)7：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, indoor heat exchanger first end temperature t is being got7With indoor heat exchanger middle portion temperature t6Afterwards, under State formula (7) generation degree of superheat Δ t7：
Δt7=t7-t6 (7)
Getting degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Afterwards, interior can be generated according to above-mentioned formula (6) to change The modifying factor D of hot device first end refrigerant enthalpy7, saturation under suction temperature then can be generated according to above-mentioned formula (5) and is freezed The enthalpy h of agentAir-breathing saturation。
Finally, according to the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7With the enthalpy of saturation refrigerant hAir-breathing saturationGenerate refrigerant enthalpy h7, h7=D7·hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
In addition, the refrigerant enthalpy h for exhaust outlet in compressor2, when the current working of air conditioner is cooling condition, The refrigerant superheat of the exhaust outlet of compressor, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined2。
According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the system of exhaust outlet The enthalpy h of cryogen2Specifically include：Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3, and according to outdoor heat exchanger Middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation, then according to the exhaust outlet of exhaust outlet in compressor Temperature t2With outdoor heat exchanger middle portion temperature t3Generate discharge superheat Δ t2, subsequently according to discharge superheat Δ t2And outdoor Heat exchanger middle portion temperature t3Generate the modifying factor D of exhaust outlet refrigerant enthalpy2, finally according to modifying factor D2, under delivery temperature The enthalpy h of saturation refrigerantIt is vented saturationGenerate the enthalpy h of the refrigerant of exhaust outlet2。
Further, the modifying factor D of exhaust outlet refrigerant enthalpy is generated according to below equation (8)2：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, room can be obtained by being disposed in the outdoor the temperature sensor (as shown in Figure 1 03) in the middle part of heat exchanger External heat exchanger middle portion temperature t3。
The exhaust port temperatures t of exhaust outlet in compressor is got2With outdoor heat exchanger middle portion temperature t3Afterwards, can be under State formula (9) generation discharge superheat Δ t2：
Δt2=t2-t3 (9)
Getting discharge superheat Δ t2With outdoor heat exchanger middle portion temperature t3Afterwards, generated and be vented according to above-mentioned formula (8) The modifying factor D of mouth refrigerant enthalpy2, then according to the enthalpy of saturation refrigerant under following formula (10) generation delivery temperature hIt is vented saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Finally, according to the modifying factor D of exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturation Generate the enthalpy h of the refrigerant of exhaust outlet2, h2=D2·hIt is vented saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of outdoor heat exchanger first end4, when the current working of air conditioner is cooling condition, room The refrigerant supercooling of external heat exchanger first end, it can directly calculate the refrigerant enthalpy h of outdoor heat exchanger first end4, i.e. according to The refrigerant enthalpy h of lower formula (11) generation outdoor heat exchanger first end4：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
In addition, based on same principle, the gaseous refrigerant enthalpy h for filling into compressor8’With the liquid system of flash vessel Cryogen enthalpy h8”, the gaseous refrigerant enthalpy h of compressor can be calculated by following formula (12)8’, pass through following formula (13) the liquid refrigerant enthalpy h of flash vessel is calculated8”。
Wherein, a1-a5For the saturation region coefficient corresponding to refrigerant, c1-c4For fauna number is subcooled corresponding to refrigerant.
It should be noted that saturation region coefficient, overheated zone coefficient and supercooling fauna number corresponding to above-mentioned refrigerant and system The species of cryogen is relevant, and R410A refrigerants and saturation region coefficient, overheated zone corresponding to R32 refrigerants are respectively illustrated in table 1 Coefficient and supercooling fauna number：
Table 1
Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, is examined with calculating each temperature The refrigerant enthalpy of measuring point.
In other embodiments of the invention, the result of calculation of software can be also directly invoked, or is obtained by other approach The refrigerant enthalpy of each temperature detecting point.For example, can also be according to sky when the current working of air conditioner is cooling condition Adjust low pressure, the gas returning port temperature t in device1, indoor heat exchanger first end temperature t7Respectively obtain the refrigerant enthalpy of gas returning port h1With the refrigerant enthalpy h of indoor heat exchanger first end7, and can be according to the high-pressure in air conditioner, exhaust port temperatures t2, room External heat exchanger first end temperature t4Respectively obtain the refrigerant enthalpy h of exhaust outlet2With the refrigerant enthalpy of outdoor heat exchanger first end h4, and saturated gas enthalpy h under the state can be obtained according to tonifying Qi temperature or pressure8’And saturated liquid enthalpy h8”。
S105, according to the power of compressor, the housing heat dissipation capacity Q of compressorloss, gas returning port refrigerant enthalpy h1, exhaust The enthalpy h of the refrigerant of mouth2, outdoor heat exchanger first end refrigerant enthalpy h4, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”Generate the refrigerating capacity of air conditioner.
According to one embodiment of present invention, the refrigerating capacity of air conditioner can be generated according to below equation (14)：
Wherein, QRefrigerating capacityFor Air conditioner refrigerating capacity, PCompressorFor compressor horsepower.
S106, the efficiency of air conditioner is generated according to air conditioner power consumption and refrigerating capacity.
Because the current working of air conditioner is cooling condition, thus can be generated according to air conditioner power consumption and refrigerating capacity empty The refrigeration efficiency of device is adjusted, specifically, the refrigeration efficiency of air conditioner is the ratio between the refrigerating capacity of air conditioner and power consumption, i.e. EER= QRefrigerating capacity/PPower consumption。
, can also be according to operation shape of the refrigeration efficiency of air conditioner to current air conditioner after the refrigeration efficiency of generation air conditioner State is adjusted.For example, the power of compressor can be improved when the refrigeration efficiency of air conditioner is relatively low, to improve air conditioner Refrigerating capacity, and the energy consumption of relative reduction air conditioner, so as to save, additionally it is possible to improve the comfortableness of user.
To sum up, the efficiency computational methods of air conditioner according to embodiments of the present invention, the first current working of acquisition air conditioner, The housing heat dissipation capacity of the power of compressor, air conditioner power consumption and compressor, and obtain the return-air of gas returning port in compressor The exhaust port temperatures of exhaust outlet, the outdoor heat exchanger first end temperature of outdoor heat exchanger first end, interior in mouth temperature, compressor The indoor heat exchanger first end temperature of heat exchanger first end and the tonifying Qi temperature of compressor tonifying Qi entrance.When the current work of air conditioner When condition is cooling condition, the refrigerant enthalpy of above-mentioned each temperature detecting point is generated according to the temperature of above-mentioned each temperature detecting point Value, the housing heat dissipation capacity of power, compressor then in conjunction with compressor, the refrigerant enthalpy and sky of above-mentioned each temperature detecting point Device power consumption is adjusted to obtain the efficiency of air conditioner.Thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating root Optimize the running status of air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and improve the purpose of refrigeration.
In addition, embodiments of the invention also proposed a kind of air conditioner, it includes memory, processor and is stored in storage On device and the computer program that can run on a processor, during computing device computer program, the above-mentioned implementation of the present invention is realized The efficiency computational methods for the air conditioner that example proposes.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.
In addition, embodiments of the invention also proposed a kind of non-transitorycomputer readable storage medium, it is stored thereon with Computer program, realize that the efficiency for the air conditioner that the above embodiment of the present invention proposes calculates when computer program is executed by processor Method.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of refrigeration.
The air conditioner and its efficiency computational methods of above-described embodiment can detect the refrigeration efficiency of air conditioner, to detect air-conditioning The heat efficiency of device, the present invention also propose the efficiency computational methods of another air conditioner.
Fig. 3 is the flow chart of the efficiency computational methods of air conditioner in accordance with another embodiment of the present invention.As shown in figure 3, The efficiency computational methods of the air conditioner of the embodiment of the present invention may include following steps：
S201, obtain the current working of air conditioner, the power of compressor and air conditioner power consumption.
Specifically, the current working of air conditioner, the power of compressor can be monitored in real time by the electric-control system of air conditioner PCompressorWith air conditioner power consumption PPower consumption。
S202, obtain the housing heat dissipation capacity Q of compressorloss；
According to one embodiment of present invention, the housing heat dissipation capacity Q of compressor can be calculated by convection current, radiation formulaloss, The housing heat dissipation capacity Q of compressor can be specifically generated according to following formula (15)loss：
Qloss=5.67 × 10-8×ACompressor((t2+273.15)4-(t8+273.15)4+(9.4+0.052×(t2-t8))× ACompressor×(t2-t8) (15)
Wherein, ACompressorFor the surface area of compressor housing, it can wait acquisition by looking into pressure contracting type number；t2For compressor The exhaust port temperatures of middle exhaust outlet, it can be by setting the temperature sensor (as shown in Figure 1 02) of exhaust outlet within the compressor Detection obtains；t8For the tonifying Qi temperature of compressor tonifying Qi entrance, it can be by being arranged on the TEMP of compressor tonifying Qi entrance Device (as shown in Figure 1 08) detection obtains.
S203, obtain the gas returning port temperature t of gas returning port in compressor1, in compressor exhaust outlet exhaust port temperatures t2, room Outdoor heat exchanger middle portion temperature t in the middle part of external heat exchanger3, the end of indoor heat exchanger second the second end of indoor heat exchanger temperature t5, room The indoor heat exchanger first end temperature t of interior heat exchanger first end7With the tonifying Qi temperature t of compressor tonifying Qi entrance8, wherein, gas returning port Temperature t1According to outdoor heat exchanger middle portion temperature t3Generated with the running frequency f of compressor.
In an embodiment of the present invention, can be by setting temperature sensor respectively in corresponding temperature test point to obtain the temperature Spend the temperature of test point.
Specifically, as shown in figure 1, can be by setting the temperature sensor of exhaust outlet within the compressor (as shown in Figure 1 02) exhaust port temperatures t is obtained2；Room is obtained by being disposed in the outdoor the temperature sensor (as shown in Figure 1 03) in the middle part of heat exchanger External heat exchanger middle portion temperature t3；Obtained by the temperature sensor (as shown in Figure 1 05) for being disposed in the interior the end of heat exchanger second Take the second end of indoor heat exchanger temperature t5；It is (as shown in Figure 1 by the temperature sensor for being disposed in the interior heat exchanger first end 07) indoor heat exchanger first end temperature t is obtained7；By being arranged on the temperature sensor of compressor tonifying Qi entrance (as shown in Figure 1 08) obtain compressor tonifying Qi entrance tonifying Qi temperature t8.Then can be according to outdoor heat exchanger middle portion temperature t3With the fortune of compressor Line frequency f generation gas returning port temperature t1。
Wherein, above-mentioned each temperature sensor effectively contacts with the refrigerant tube wall of corresponding temperature test point, is testing During the temperature of refrigerant tube wall, refrigerant tube wall can take Insulation, and the installation site of temperature sensor is as close to temperature Spend test point.For example, temperature sensor can be arranged on to corresponding temperature detecting point and be close to copper pipe, and by being incubated glue Band is wound sealing to copper pipe.Thereby, it is possible to improve the reliability and accuracy of temperature detection.
According to one embodiment of present invention, can be according to following formula when the current working of air conditioner is heating condition (15) gas returning port temperature t is generated1：
t1=c*t3+d*f (16)
Wherein, f is compressor operating frequency, and c, d are fitting coefficient, and c, d can obtain according to lot of experimental data, can be led to The electric-control system for crossing air conditioner monitors the running frequency of compressor in real time.
S204, when the current working of air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in compressor1 Generate the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the refrigerant of exhaust outlet Enthalpy h2, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generate the refrigeration at the end of indoor heat exchanger second Agent enthalpy h5, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7Generate the system of indoor heat exchanger first end Cryogen enthalpy h7With the tonifying Qi temperature t according to compressor tonifying Qi entrance8Generation fills into the gaseous refrigerant enthalpy of compressor respectively h8’With the liquid refrigerant enthalpy h of flash vessel8”。
Herein it should be noted that when the current working of air conditioner is heating condition, outdoor heat exchanger makees evaporator, room Interior heat exchanger makees condenser, and indoor heat exchanger first end is condenser inlet, and the end of indoor heat exchanger second is condensator outlet.
Specifically, during air conditioner works, because the state of the refrigerant of different temperatures test point is different, therefore The enthalpy of the refrigerant of different temperatures test point is different.In one embodiment of the invention, rule of thumb formula can calculate To the enthalpy of refrigerant.
Illustrate that rule of thumb formula obtains the refrigerant enthalpy h of gas returning port separately below1, exhaust outlet refrigerant enthalpy h2, the end of indoor heat exchanger second refrigerant enthalpy h5, indoor heat exchanger first end refrigerant enthalpy h7, fill into compressor Gaseous refrigerant enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”Detailed process.
Wherein, for the refrigerant enthalpy h of gas returning port in compressor1, when the current working of air conditioner is heating condition, The refrigerant superheat of the gas returning port of compressor, the refrigerant enthalpy h that suction superheat calculates gas returning port can be combined1。
According to one embodiment of present invention, according to the gas returning port temperature t of gas returning port in compressor1Generate the system of gas returning port Cryogen enthalpy h1Specifically include：According to gas returning port temperature t1With outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1, and According to suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Generate the modifying factor D of gas returning port refrigerant enthalpy1, and According to outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation, finally according to gas returning port system The modifying factor D of cryogen enthalpy1, under suction temperature saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigerant enthalpy h of gas returning port1。
Further, the modifying factor D of gas returning port refrigerant enthalpy is generated according to below equation (17)1：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, gas returning port temperature t is being got1With outdoor heat exchanger middle portion temperature t3Afterwards, according to following formula (18) Generate suction superheat Δ t1：
Δt1=t1-t3 (18)
Getting suction superheat Δ t1With outdoor heat exchanger middle portion temperature t3Afterwards, according to above-mentioned formula (17) gas returning port The modifying factor D of refrigerant enthalpy1, then can be according to the enthalpy of saturation refrigerant under following formula (19) generation suction temperature hAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Finally, according to the modifying factor D of gas returning port refrigerant enthalpy1, under suction temperature saturation refrigerant enthalpy hAir-breathing saturation Generate the refrigerant enthalpy h of gas returning port1, h1=D1·hAir-breathing saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h of exhaust outlet in compressor2, when the current working of air conditioner is heating condition, compression The refrigerant superheat of the exhaust outlet of machine, the refrigerant enthalpy h that discharge superheat calculates exhaust outlet can be combined2。
According to one embodiment of present invention, according to the exhaust port temperatures t of exhaust outlet in compressor2Generate the system of exhaust outlet The enthalpy h of cryogen2Specifically include：Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6, and according to indoor heat exchanger The indoor heat exchanger middle portion temperature t at middle part6With the exhaust port temperatures t of exhaust outlet in compressor2Generate discharge superheat Δ t2, so Afterwards according to discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Generate the modifying factor D of exhaust outlet refrigerant enthalpy2, so Afterwards according to outdoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation, finally according to exhaust outlet The modifying factor D of refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigerant enthalpy of exhaust outlet h2。
Further, the modifying factor D of exhaust outlet refrigerant enthalpy is generated according to below equation (20)2：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, room can be obtained by being disposed in the interior the temperature sensor (as shown in Figure 1 06) in the middle part of heat exchanger Interior heat exchanger middle portion temperature t6。
Getting the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6With the exhaust outlet of exhaust outlet in compressor Temperature t2Afterwards, discharge superheat Δ t can be generated according to following formula (21)2：
Δt2=t2-t6 (21)
Getting discharge superheat Δ t2With indoor heat exchanger middle portion temperature t6Afterwards, generated and arranged according to above-mentioned formula (20) The modifying factor D of gas port refrigerant enthalpy2, then can be according to the enthalpy of saturation refrigerant under following formula (22) generation delivery temperature Value hIt is vented saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
Finally, according to the modifying factor D of exhaust outlet refrigerant enthalpy2, under delivery temperature saturation refrigerant enthalpy hIt is vented saturation Generate the refrigerant enthalpy h of exhaust outlet2, h2=D2·hIt is vented saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
Similarly, for the refrigerant enthalpy h of indoor heat exchanger first end7, when the current working of air conditioner is heating work During condition, the refrigerant superheat of indoor heat exchanger first end, the position refrigerant superheat degree can be combined and calculate indoor heat exchanger first The refrigerant enthalpy h at end7。
According to one embodiment of present invention, according to the indoor heat exchanger first end temperature t of indoor heat exchanger first end7It is raw Into the refrigerant enthalpy h of indoor heat exchanger first end7Specifically include：Temperature in the middle part of indoor heat exchanger in the middle part of indoor heat exchanger Spend t6With indoor heat exchanger first end temperature t7Generate degree of superheat Δ t7, and according to degree of superheat Δ t7With temperature in the middle part of indoor heat exchanger Spend t6Generate the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7, and according to indoor heat exchanger first end refrigerant The modifying factor D of enthalpy7, under delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate refrigerant enthalpy h7。
Further, the modifying factor D of indoor heat exchanger first end refrigerant enthalpy is generated according to below equation (23)7：
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
Specifically, the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger is being got6With indoor heat exchanger first Hold temperature t7Afterwards, degree of superheat Δ t is generated according to following formula (24)7：
Δt7=t7-t6 (24)
Getting degree of superheat Δ t7With indoor heat exchanger middle portion temperature t6Afterwards, can be generated according to above-mentioned formula (23) indoor The modifying factor D of heat exchanger first end refrigerant enthalpy7, then saturation system under delivery temperature can be generated according to above-mentioned formula (22) The enthalpy h of cryogenIt is vented saturation。
Finally, according to the modifying factor D of indoor heat exchanger first end refrigerant enthalpy7With the enthalpy of saturation refrigerant hIt is vented saturationGenerate refrigerant enthalpy h7, h7=D7·hIt is vented saturation+d7, wherein, d7For overheated zone coefficient corresponding to refrigerant.
For the refrigerant enthalpy h at the end of indoor heat exchanger second5, when the current working of air conditioner is heating condition, room The refrigerant supercooling at the interior end of heat exchanger second, it can directly calculate the refrigerant enthalpy h at the end of indoor heat exchanger second5, i.e. according to Lower formula meter (25) calculates the refrigerant enthalpy h at the end of indoor heat exchanger second5：
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
In addition, in one embodiment of the invention, the gaseous refrigerant enthalpy h for filling into compressor8’And flash vessel Liquid refrigerant enthalpy h8”, the gaseous refrigerant enthalpy h of compressor can be calculated by above-mentioned formula (12)8’, by upper State the liquid refrigerant enthalpy h that flash vessel is calculated in formula (13)8”, i.e., Wherein, a1-a5For the saturation region coefficient corresponding to refrigerant, c1-c4For mistake corresponding to refrigerant Cold-zone coefficient.
It should be noted that saturation region coefficient, overheated zone coefficient and supercooling fauna number corresponding to above-mentioned refrigerant and system The species of cryogen is relevant, respectively illustrated in above-mentioned table 1 R410A refrigerants and saturation region coefficient corresponding to R32 refrigerants, Overheated zone coefficient and supercooling fauna number.
Thus, each coefficient value can be obtained according to the species of refrigerant and the corresponding relation of such as table 1, is examined with calculating each temperature The refrigerant enthalpy of measuring point.
In other embodiments of the invention, the result of calculation of software can be also directly invoked, or is obtained by other approach The refrigerant enthalpy of each temperature detecting point.For example, can also be according to sky when the current working of air conditioner is heating condition Adjust high-pressure, the gas returning port temperature t in device1, indoor heat exchanger first end temperature t7Respectively obtain the refrigerant enthalpy of gas returning port h1With the refrigerant enthalpy h of indoor heat exchanger first end7, and can be according to the high-pressure in air conditioner, exhaust port temperatures t2, room Interior the second end of heat exchanger temperature t5Respectively obtain the refrigerant enthalpy h of exhaust outlet2With the refrigerant enthalpy at the end of indoor heat exchanger second h5, and saturated gas enthalpy h under the state can be obtained according to tonifying Qi temperature or pressure8’And saturated liquid enthalpy h8”。
S205, according to the power of compressor, the housing heat dissipation capacity Q of compressorloss, gas returning port refrigerant enthalpy h1, exhaust The enthalpy h of the refrigerant of mouth2, the end of indoor heat exchanger second refrigerant enthalpy h5, indoor heat exchanger first end refrigerant enthalpy h7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy h of flash vessel8”Generate the heating capacity of air conditioner.
According to one embodiment of present invention, the heating capacity of air conditioner is generated according to equation below (26)：
Wherein, QHeating capacityFor heating capacity of air conditioner, PCompressorFor compressor horsepower.
S206, the efficiency of air conditioner is generated according to air conditioner power consumption and heating capacity.
Because the current working of air conditioner is heating condition, thus can be generated according to air conditioner power consumption and heating capacity empty The heat efficiency of device is adjusted, specifically, the heat efficiency of air conditioner is the ratio between the heating capacity of air conditioner and power consumption, i.e. COP= QHeating capacity/PPower consumption。
, can also be according to operation shape of the heat efficiency of air conditioner to current air conditioner after the heat efficiency of generation air conditioner State is adjusted.For example, the power of compressor can be improved when the heat efficiency of air conditioner is relatively low, to improve air conditioner Heating capacity, and the energy consumption of relative reduction air conditioner, so as to save, additionally it is possible to improve the comfortableness of user.
To sum up, the efficiency computational methods of air conditioner according to embodiments of the present invention, the first current working of acquisition air conditioner, The housing heat dissipation capacity of the power of compressor, air conditioner power consumption and compressor, and obtain the return-air of gas returning port in compressor The exhaust port temperatures of exhaust outlet, the second end of indoor heat exchanger temperature at the end of indoor heat exchanger second, interior in mouth temperature, compressor The indoor heat exchanger first end temperature of heat exchanger first end and the tonifying Qi temperature of compressor tonifying Qi entrance.When the current work of air conditioner When condition is heating condition, the refrigerant enthalpy of above-mentioned each temperature detecting point is generated according to the temperature of above-mentioned each temperature detecting point Value, the housing heat dissipation capacity of power, compressor then in conjunction with compressor, the refrigerant enthalpy and sky of above-mentioned each temperature detecting point Device power consumption is adjusted to obtain the efficiency of air conditioner.Thereby, it is possible to real-time and accurately detect the efficiency of air conditioner, consequently facilitating root Optimize the running status of air conditioner according to the real-time energy efficiency of air conditioner, reach energy-conservation and improve the purpose of heating effect.
In addition, embodiments of the invention also proposed another air conditioner, it includes memory, processor and is stored in On reservoir and the computer program that can run on a processor, during computing device computer program, the invention described above reality is realized Apply the efficiency computational methods of the air conditioner of example proposition.
Air conditioner according to embodiments of the present invention, real-time and accurately efficiency can be detected.
In addition, embodiments of the invention also proposed another non-transitorycomputer readable storage medium, store thereon There is computer program, the efficiency meter for the air conditioner that the above embodiment of the present invention proposes is realized when computer program is executed by processor Calculation method.
Non-transitorycomputer readable storage medium according to embodiments of the present invention, by the computer journey for performing its storage Sequence, the efficiency of air conditioner can be real-time and accurately detected, consequently facilitating optimizing air conditioner according to the real-time energy efficiency of air conditioner Running status, reach energy-conservation and improve the purpose of heating effect.
In the description of the invention, it is to be understood that term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", " under ", "front", "rear", "left", "right", " vertical ", " level ", " top ", " bottom ", " interior ", " outer ", " up time The orientation or position relationship of the instruction such as pin ", " counterclockwise ", " axial direction ", " radial direction ", " circumference " be based on orientation shown in the drawings or Position relationship, it is for only for ease of and describes the present invention and simplify description, rather than indicates or imply that signified device or element must There must be specific orientation, with specific azimuth configuration and operation, therefore be not considered as limiting the invention.
In addition, term " first ", " second " are only used for describing purpose, and it is not intended that instruction or hint relative importance Or the implicit quantity for indicating indicated technical characteristic.Thus, define " first ", the feature of " second " can be expressed or Implicitly include one or more this feature.In the description of the invention, " multiple " are meant that two or more, Unless otherwise specifically defined.
In the present invention, unless otherwise clearly defined and limited, term " installation ", " connected ", " connection ", " fixation " etc. Term should be interpreted broadly, for example, it may be fixedly connected or be detachably connected, or integrally；Can be that machinery connects Connect or electrically connect；Can be joined directly together, can also be indirectly connected by intermediary, can be in two elements The connection in portion or the interaction relationship of two elements.For the ordinary skill in the art, can be according to specific feelings Condition understands the concrete meaning of above-mentioned term in the present invention.
In the present invention, unless otherwise clearly defined and limited, fisrt feature can be with "above" or "below" second feature It is that the first and second features directly contact, or the first and second features pass through intermediary mediate contact.Moreover, fisrt feature exists Second feature " on ", " top " and " above " but fisrt feature are directly over second feature or oblique upper, or be merely representative of Fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " lower section " and " below " can be One feature is immediately below second feature or obliquely downward, or is merely representative of fisrt feature level height and is less than second feature.
In the description of this specification, reference term " one embodiment ", " some embodiments ", " example ", " specifically show The description of example " or " some examples " etc. means specific features, structure, material or the spy for combining the embodiment or example description Point is contained at least one embodiment or example of the present invention.In this manual, to the schematic representation of above-mentioned term not Identical embodiment or example must be directed to.Moreover, specific features, structure, material or the feature of description can be with office Combined in an appropriate manner in one or more embodiments or example.In addition, in the case of not conflicting, the skill of this area Art personnel can be tied the different embodiments or example and the feature of different embodiments or example described in this specification Close and combine.
Although embodiments of the invention have been shown and described above, it is to be understood that above-described embodiment is example Property, it is impossible to limitation of the present invention is interpreted as, one of ordinary skill in the art within the scope of the invention can be to above-mentioned Embodiment is changed, changed, replacing and modification.

Claims (24)

1. the efficiency computational methods of a kind of air conditioner, it is characterised in that comprise the following steps：
Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；
Obtain the housing heat dissipation capacity Q of compressorloss；
Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust port temperatures t2, outdoor heat exchange The outdoor heat exchanger first end temperature t of device first end4, indoor heat exchanger first end indoor heat exchanger first end temperature t7And pressure The tonifying Qi temperature t of contracting machine tonifying Qi entrance8, wherein, the gas returning port temperature t1The indoor heat exchanger first end temperature t7And compression The running frequency f generations of machine；
When the current working of the air conditioner is cooling condition, according to the gas returning port temperature t of gas returning port in the compressor1It is raw Into the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate the refrigerant of exhaust outlet Enthalpy h2, according to the outdoor heat exchanger first end temperature t of the outdoor heat exchanger first end4Generate outdoor heat exchanger first end Refrigerant enthalpy h4, according to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end7Generate indoor heat exchanger The refrigerant enthalpy h of first end7With the tonifying Qi temperature t according to the compressor tonifying Qi entrance8Generation fills into the gas of compressor respectively State refrigerant enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”；
According to the power of the compressor, the housing heat dissipation capacity Q of the compressorloss, the gas returning port refrigerant enthalpy h1、 The enthalpy h of the refrigerant of the exhaust outlet2, the outdoor heat exchanger first end refrigerant enthalpy h4, the indoor heat exchanger The refrigerant enthalpy h of one end7, the gaseous refrigerant enthalpy h for filling into compressor8’With the liquid refrigerant enthalpy of the flash vessel Value h8”Generate the refrigerating capacity of air conditioner；And
The efficiency of the air conditioner is generated according to the air conditioner power consumption and the refrigerating capacity.
2. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that described to be returned according in the compressor The gas returning port temperature t of gas port1Generate the refrigerant enthalpy h of the gas returning port1Specifically include：
Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；
According to the gas returning port temperature t1With the indoor heat exchanger middle portion temperature t6Generate suction superheat Δ t1；
According to the indoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；
According to the suction superheat Δ t1With indoor heat exchanger middle portion temperature t6Generate the modifying factor of gas returning port refrigerant enthalpy D1；
According to the modifying factor D of the gas returning port refrigerant enthalpy1, the saturation refrigerant enthalpy hAir-breathing saturationGenerate the refrigeration Agent enthalpy h1。
3. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that the suction is generated according to below equation The enthalpy h of saturation refrigerant at a temperature of gasAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
4. the efficiency computational methods of air conditioner as claimed in claim 2, it is characterised in that returned according to below equation generation The modifying factor D of gas port refrigerant enthalpy1：
<mrow> <msub> <mi>D</mi> <mn>1</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
5. the efficiency computational methods of air conditioner as claimed in claim 3, it is characterised in that described according to the indoor heat exchanger The indoor heat exchanger first end temperature t of first end7Generate the refrigerant enthalpy h of the indoor heat exchanger first end7Specifically include：
According to the indoor heat exchanger first end temperature t7With the indoor heat exchanger middle portion temperature t6Generate degree of superheat Δ t7；
According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end refrigerant enthalpy Modifying factor D7；
According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy7With the enthalpy h of the saturation refrigerantAir-breathing saturation Generate the refrigerant enthalpy h7。
6. the efficiency computational methods of air conditioner as claimed in claim 5, it is characterised in that the room is generated according to below equation The modifying factor D of interior heat exchanger first end refrigerant enthalpy7：
<mrow> <msub> <mi>D</mi> <mn>7</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
7. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that described to be arranged according in the compressor The exhaust port temperatures t of gas port2Generate the enthalpy h of the refrigerant of the exhaust outlet2Specifically include：
Obtain the outdoor heat exchanger middle portion temperature t in the middle part of outdoor heat exchanger3；
According to the outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；
According to the exhaust port temperatures t of exhaust outlet in the compressor2With the outdoor heat exchanger middle portion temperature t3Generate discharge superheat Spend Δ t2；
According to the discharge superheat Δ t2With the outdoor heat exchanger middle portion temperature t3Generate the amendment of exhaust outlet refrigerant enthalpy Factor D2；
According to the modifying factor D2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationGenerate the refrigeration of the exhaust outlet The enthalpy h of agent2。
8. the efficiency computational methods of air conditioner as claimed in claim 7, it is characterised in that the row is generated according to below equation The modifying factor D of gas port refrigerant enthalpy2：
<mrow> <msub> <mi>D</mi> <mn>2</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>3</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>3</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>3</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>3</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
9. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that the room is generated according to below equation The refrigerant enthalpy h of external heat exchanger first end4：
<mrow> <msub> <mi>h</mi> <mn>4</mn> </msub> <mo>=</mo> <msub> <mi>c</mi> <mn>1</mn> </msub> <mo>+</mo> <msub> <mi>c</mi> <mn>2</mn> </msub> <msub> <mi>t</mi> <mn>4</mn> </msub> <mo>+</mo> <msub> <mi>c</mi> <mn>3</mn> </msub> <msubsup> <mi>t</mi> <mn>4</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>c</mi> <mn>4</mn> </msub> <msubsup> <mi>t</mi> <mn>4</mn> <mn>3</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
10. the efficiency computational methods of air conditioner as claimed in claim 1, it is characterised in that according to generating below equation The refrigerating capacity of air conditioner：
Wherein, QRefrigerating capacityFor the Air conditioner refrigerating capacity, PCompressorFor compressor horsepower.
11. a kind of air conditioner, it is characterised in that including memory, processor and be stored on the memory and can be described The computer program run on processor, described in the computing device during computer program, realize as in claim 1-10 Any described method.
12. a kind of non-transitorycomputer readable storage medium, is stored thereon with computer program, it is characterised in that the meter The method as described in any in claim 1-10 is realized when calculation machine program is executed by processor.
13. the efficiency computational methods of a kind of air conditioner, it is characterised in that comprise the following steps：
Obtain current working, the power and air conditioner power consumption of compressor of air conditioner；
Obtain the housing heat dissipation capacity Q of compressorloss；
Obtain the gas returning port temperature t of gas returning port in compressor1, in the compressor exhaust outlet exhaust port temperatures t2, outdoor heat exchange Outdoor heat exchanger middle portion temperature t in the middle part of device3, the end of indoor heat exchanger second the second end of indoor heat exchanger temperature t5, indoor heat exchange The indoor heat exchanger first end temperature t of device first end7With the tonifying Qi temperature t of compressor tonifying Qi entrance8, wherein, the gas returning port temperature Spend t1According to the outdoor heat exchanger middle portion temperature t3Generated with the running frequency f of compressor；
When the current working of the air conditioner is heating condition, according to the gas returning port temperature t of gas returning port in the compressor1It is raw Into the refrigerant enthalpy h of gas returning port1, according to the exhaust port temperatures t of exhaust outlet in the compressor2Generate the refrigerant of exhaust outlet Enthalpy h2, according to the second end of indoor heat exchanger temperature t at the end of indoor heat exchanger second5Generate the end of indoor heat exchanger second Refrigerant enthalpy h5, according to the indoor heat exchanger first end temperature t of the indoor heat exchanger first end7Generate indoor heat exchanger The refrigerant enthalpy h of first end7With the tonifying Qi temperature t according to the compressor tonifying Qi entrance8Generation fills into the gas of compressor respectively State refrigerant enthalpy h8’With the liquid refrigerant enthalpy h of flash vessel8”；
According to the power of the compressor, the housing heat dissipation capacity Q of the compressorloss, the gas returning port refrigerant enthalpy h1、 The enthalpy h of the refrigerant of the exhaust outlet2, the end of indoor heat exchanger second refrigerant enthalpy h5, the indoor heat exchanger The refrigerant enthalpy h of one end7, fill into the gaseous refrigerant enthalpy h of compressor8’With the liquid refrigerant enthalpy of the flash vessel h8”Generate the heating capacity of air conditioner；And
The efficiency of the air conditioner is generated according to the air conditioner power consumption and the heating capacity.
14. the efficiency computational methods of air conditioner as claimed in claim 13, it is characterised in that described according in the compressor The gas returning port temperature t of gas returning port1Generate the refrigerant enthalpy h of the gas returning port1Specifically include：
According to the gas returning port temperature t1With the outdoor heat exchanger middle portion temperature t3Generate suction superheat Δ t1；
According to the suction superheat Δ t1With the outdoor heat exchanger middle portion temperature t3Generate the amendment of gas returning port refrigerant enthalpy Factor D1；
According to the outdoor heat exchanger middle portion temperature t3Generate the enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation；
According to the modifying factor D of the gas returning port refrigerant enthalpy1, under the suction temperature saturation refrigerant enthalpy hAir-breathing saturationIt is raw Into the refrigerant enthalpy h of the gas returning port1。
15. the efficiency computational methods of air conditioner as claimed in claim 14, it is characterised in that according to generating below equation The enthalpy h of saturation refrigerant under suction temperatureAir-breathing saturation：
Wherein, a1-a5For saturation region coefficient corresponding to refrigerant.
16. the efficiency computational methods of air conditioner as claimed in claim 14, it is characterised in that according to generating below equation The modifying factor D of gas returning port refrigerant enthalpy1：
<mrow> <msub> <mi>D</mi> <mn>1</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>3</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>3</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>3</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>1</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>3</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
17. the efficiency computational methods of air conditioner as claimed in claim 14, it is characterised in that described according in the compressor The exhaust port temperatures t of exhaust outlet2Generate the enthalpy h of the refrigerant of the exhaust outlet2Specifically include：
Obtain the indoor heat exchanger middle portion temperature t in the middle part of indoor heat exchanger6；
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the exhaust outlet temperature of exhaust outlet in the compressor Spend t2Generate discharge superheat Δ t2；
According to the discharge superheat Δ t2With the indoor heat exchanger middle portion temperature t6Generate the amendment of exhaust outlet refrigerant enthalpy Factor D2；
According to the outdoor heat exchanger middle portion temperature t6Generate the enthalpy h of saturation refrigerant under delivery temperatureIt is vented saturation；
According to the modifying factor D of the exhaust outlet refrigerant enthalpy2, under the delivery temperature saturation refrigerant enthalpy hIt is vented saturationIt is raw Into the refrigerant enthalpy h of the exhaust outlet2。
18. the efficiency computational methods of the air conditioner described in claim 17, it is characterised in that the row is generated according to below equation The modifying factor D of gas port refrigerant enthalpy2：
<mrow> <msub> <mi>D</mi> <mn>2</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>2</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
19. the efficiency computational methods of air conditioner as claimed in claim 17, it is characterised in that described according to the indoor heat exchange The indoor heat exchanger first end temperature t of device first end7Generate the refrigerant enthalpy h of the indoor heat exchanger first end7Specific bag Include：
According to the indoor heat exchanger middle portion temperature t in the middle part of the indoor heat exchanger6With the indoor heat exchanger first end temperature t7It is raw Into degree of superheat Δ t7；
According to the degree of superheat Δ t7With the indoor heat exchanger middle portion temperature t6Generate indoor heat exchanger first end refrigerant enthalpy Modifying factor D7；
According to the modifying factor D of the indoor heat exchanger first end refrigerant enthalpy7, saturation refrigerant under the delivery temperature Enthalpy hIt is vented saturationGenerate the refrigerant enthalpy h7。
20. the efficiency computational methods of air conditioner as claimed in claim 19, it is characterised in that according to generating below equation The modifying factor D of indoor heat exchanger first end refrigerant enthalpy7：
<mrow> <msub> <mi>D</mi> <mn>7</mn> </msub> <mo>=</mo> <mn>1</mn> <mo>+</mo> <msub> <mi>d</mi> <mn>1</mn> </msub> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>2</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <mo>+</mo> <msub> <mi>d</mi> <mn>3</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>4</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msub> <mi>t</mi> <mn>6</mn> </msub> <mo>+</mo> <msub> <mi>d</mi> <mn>5</mn> </msub> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>d</mi> <mn>6</mn> </msub> <msup> <mrow> <mo>(</mo> <msub> <mi>&amp;Delta;t</mi> <mn>7</mn> </msub> <mo>)</mo> </mrow> <mn>2</mn> </msup> <msubsup> <mi>t</mi> <mn>6</mn> <mn>2</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, d1-d6For overheated zone coefficient corresponding to refrigerant.
21. the efficiency computational methods of air conditioner as claimed in claim 13, it is characterised in that according to calculating below equation The refrigerant enthalpy h at the end of indoor heat exchanger second5：
<mrow> <msub> <mi>h</mi> <mn>5</mn> </msub> <mo>=</mo> <msub> <mi>c</mi> <mn>1</mn> </msub> <mo>+</mo> <msub> <mi>c</mi> <mn>2</mn> </msub> <msub> <mi>t</mi> <mn>5</mn> </msub> <mo>+</mo> <msub> <mi>c</mi> <mn>3</mn> </msub> <msubsup> <mi>t</mi> <mn>5</mn> <mn>2</mn> </msubsup> <mo>+</mo> <msub> <mi>c</mi> <mn>4</mn> </msub> <msubsup> <mi>t</mi> <mn>5</mn> <mn>3</mn> </msubsup> <mo>,</mo> </mrow>
Wherein, c1-c4For fauna number is subcooled corresponding to refrigerant.
22. the efficiency computational methods of air conditioner as claimed in claim 13, it is characterised in that according to generating equation below The heating capacity of air conditioner：
Wherein, QHeating capacityFor the heating capacity of air conditioner, PCompressorFor compressor horsepower.
23. a kind of air conditioner, it is characterised in that including memory, processor and be stored on the memory and can be described The computer program run on processor, described in the computing device during computer program, realize as in claim 13-22 Any described method.
24. a kind of non-transitorycomputer readable storage medium, is stored thereon with computer program, it is characterised in that the meter The method as described in any in claim 13-22 is realized when calculation machine program is executed by processor.
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Application publication date: 20171219